Building motion for textile machines



April 20; 1954 c. GOODWIN, ET AL BUILDING MOTION. FOR TEXTILE MACHINES Filed Sept. 1'7, 1951 8 Sheets-Sheet 1 lzzvezz-tora .ll. C. GOOCZLOCR/ C. H.ZI.T]2/0rpe A ril 20, 1954 1.. c. GOODWIN ET AL 2,675,972

" BUILDING MOTION FOR TEXTILE MACHINES Filed Sept. 17,- 1951 8 Sheets-Sheet 2 L. C. Goody/LIL April 20, 1954 Q Q oonwm ET AL 2,675,972

BUILDING MOTION FOR TEXTILE MACHINES Filed Sept. .17, 1951 a Sheets-Sheet a M M a B a t QQ K 7 q} lzvvezztaz s 1.11.0. Goodwin Thor 0e I April 20, 1954 c. GOODVI/IN ET AL 2,675,972

I BUILDING MOTION FOR TEXTILE MACHINES Filed Sept. 17, 1951 8 Sheets-Sheet 4 l bvezziliol s L, C. GOOdwi April 20, 1954 L. C GOODWIN' ET AL BUILDINGMOTION FOR TEXTILE MACHINES Filed Sept. 17, 1951 L. (3. G00 d wizz/ C H.M .T.ZZOr Ee April 20, 1954 L. c. GOODWlN E-IAL 2,675,972

BUILDING MOTION FOR TEXTILE MACHINES Filed Sept. 17. 1951 8 Sheets-Sheet 6 Evan/bolus April 20, 1954 L. c. eoonwlN ET AL 2,675,972

BUILDING MOTION FOR TEXTILE MACHINES Filed Sept. 17, 1951 v I 8 Sheets-Sheet 7 Aprfl 20, 1954 L- c. GOODWIN ETAL BUILDING MOTION FOR TEXTILE MACHINES 8 Sheets-Sheet 8 Filed Sept. 17-, 1951 .Zlzzu 612223026 L C, Goodman C3 H.M.Tj2/01pe Patented Apr. 20, 1954 UNITED STATES TENT OFFICE BUILDING MOTION FOR TEXTILE MACHINES i511 company Application September 17; 1951-, Serial N 246,916

Claims priority, application Great Britain September 27, 1950 '7 Claims.

This invention relates tobuilding motions or mechanisms as used for the building or yarn packages in textile spinning, doubling, winding and like machines, such motions or mechanisms including a part which has a reciprocatory or oscillatory part which determines how the yarn is laid on the package which is being Wound and therefore the shape or build of the packages The object of the present invention is to provide an improved motion or mechanism particularly for use in machines requiring a precise or accurate travel of the reciprocator'y element without dwell or lost motion at reversals, as for example in machines dealing with rayon and like smooth yarns.

In accordance with our present invention, a reversing vane type hydraulic motor is utilised to impart oscillatory or back and forth rotary movements to a shaft to which its rotor is coupled, and such shaft gives through suitable mechanism the necessary reciprocatory movements to the part which determines how the yarn is laid on the yarn package which is being wound.

in the case of a ring spinning frame intended for rayon yarns the rotor of the reversible vane type hydraulic motor may be axially in line with a shaft carrying pihions by which racks traversing the ring rail are operated.

The point of reversal of the rotor of the vane type motor is varied so as to vary the lengths of the reciprocations or traverses of the ring rail or other part which determines how the yarn is laid on the yarn package which is being wound in order to give the desired build to such yarn package.

In the accompanying explanatory drawings:

Figure l is a diagrammatic illustration showing one form of our improved ring rail lifting or building motion applied to the ring rail of a spinning or like machine.

Figure 2 is an elevation, Figure 3 an end view looking from left to right of Figure 2, Figure 4 a sectional view on the line l-- -4 of Figure 2 and Figure 5 a longitudinal sectional elevation show ing a. vane type hydraulic motor with its reversing mechanism constructed in one convenient form for use in the building motion shown diagrammatically in Figure 1.

Figure 6 is an exploded view of the reversing valve of the hydraulic motor.

Figure 7 is a View showing the recessed plate with its stop member and the ratchet wheel with its pawl carrying arms and the pivdted arms which ride upon the recessed plate. This view is taken looking from right tolefttif-the recessed 2 plate in Figure 5, but with'parts added to make the operation of the mechanism more clear.

Figure 8 is an end view of the mechanism shown in Figure 5, but with the building motions, that is the ratchet wheel, pawls, recessed plate and associated parts removed. V

Figure 9 is a View similar to Figure 2 but with certain parts in different positions and other parts omitted to add to the clearness of the illustration.

Figures 10 and 11 are views similar to Figures 3 and 7 but showing a modified arrangement of the building motion.

Figures 12 and 13 are views similar to Figures r 10 and 11 but showing a further modified arrangement of the building motion.

Figure 14 is a view showing the parts which operate the single ended pawl and the pawl arm separating lever in the Figures 12 and 13 arrangement.

Figure 15 shows the shapes of bobbin which can be built with the Figures 12 and 13 arrangement.

Figure 16 shows the principle of the winding effected by the Figures 12 and 1S arrangement.

Figure 17 shows another form of ring rail lifting motion to which our invention can be applied.

In Figure 1, the ring rail a, in which are secured the usual, rings with travellers thereon (not shown) by which yarn is laid on revolving bobbins as b, is raised and lowered by pinions as c meshing with racks as d secured to and carrying the ring rail in the well known manner;

The pinion shaft e is oscillated or given back and forth movements about its axis by the reversing vane type hydraulic motor the vane of which is directly secured to the shaft e. g is an oil tank from which oil is drawn by a pump indicated at h and delivered under pressure, via a safety valve fitting z and a filter :i, to a reversing valve at is.

Gonstructions of the hydraulic motor and the reversing valve will be described with reference to the remaining figures of the drawings.

In Figure 4, the vane m of the hydraulic inotor is directly secured to the pinion shaft e or the rail actuating racl: and pinion device shown in Figure l, and it oscillates back and forth in the annular space it with the motor cylinder 0 arc cording as hydraulic fluid, preferably oil, is pressing upon and exhausting from its opposite sides munication either with exhaust or with the by draulic fluid supply under the control of the valve t (shown in Figure 6), which is oscillated by the mechanism to be hereinafter described. The central port 1) in the valve t is a pocket which can place either of the side ports 21), a", in the valve seat u, which lead to the ports 1', s in the abutment p, in communication with the exhaust passage q, whilst the outer ports 1/, z in the valve t, which are through ports, can pass hydraulic fluid (which enters the valve casing 7c by-the fitting 2 (Figure 2) to either of the ports 10, at in the valve seat u and so to the ports 1, s in the abutment p. The valve arrangement, which is not in itself new, serves to effect reversals of the movements of the vane m in the hydraulic motor and s oscillatory movements of the motor and pinion shaft e.

It will be appreciated by those skilled in the spinning and like arts that if the length of arouate movement of the vane m is varied, the build of the bobbin as b (Figure 1) being wound will be varied. The mechanism now to be described is designed to give varying lengths of movement of the vane m, starting from a fixed point.

The shaft 3 of the valve i (see Figures and 8) has a crank arm 4 clamped thereon, the crank pin 5 of which has a roller thereon and projects through a gap to in a fixed bridge piece ii into the gap 5 in a rocking arm I which is journalled on the part 8 (see Figure 5) carried by the end cover of the vane motor. The rocking arm I (see Figure 8) has a lug 9 thereon in which are secured two adjustable stop pins i2 and it which serve, as hereinafter described, to turn the crank arm 4 in one or other direction and so the valve shaft 3, to reverse the valve. The rocking arm 7 can take up one or other of two extreme positions as determined by the springs i 4 and I5 which have a toggle action with reference to the movements of the rocking arm. gap iii in the bridge piece ii serves to limit the movements of the crank arm.

A plate I6 (see Figures 5 and '7) which has a raised peripheral surface I! and a depressed peripheral surface [8 is secured upon a boss 59 which is rigid with the motor shaft e. A pin 2G projects from the side of the plate it (see Figure 9) and in one direction of movement of the rotor shaft e engages the stop screw i2 and so moves the rocking arm 7 from one extreme position to the other with a snap action due to the springs M, 55, which results in a movement of the valve t and the reversal of the movement of the rotor vane m.

A ratchet wheel 2! is frictionally carried on the bos i9 and it is engaged by pawls 22 and 23 on two pawl carrying arms 24 and 25 (see Figure 3). A spring 26 tends to draw the arm 25 towards the arm 25 so that it rests against a face 2'; on such arm 24.

The ratchet wheel has three arms 28, 29 and 3t pivotally mounted thereon and these have rollers thereon at their outer ends which ride under the pressure of springs 3i upon the peripheral edge of the plate It. Each arm carries an abutment piece 32 which when the roller on the arm which it is secured is on the depressed or recessed surface 18 of the plate it can engage the screw abutment, I3 (as shown at the top of Figure 7) to move the rocking arm l and through it the crank arm 4 and the valve spindle 3 in a direction to reverse the flow of hydraulic fluid to the motor in order to reverse the rotor shaft e. The pawl arm 2G is rigid with the shaft e and moves back and forth therewith.

The

If we assume in Figure 3 that the arm 26 is moving anticlockwise and carrying with it the arm 25, the ratchet wheel also will be being moved by friction, due to its method of mounting, in an anti-clockwise direction. Eventually the arm 25 will engage the adjustable stop 33 which will hold it against further movement, and through the pawl 23 the ratchet wheel .2! will be held against further movement, but the arm 2 2 will still move until the pin 26 on the plate E6 engages the stop l2 and through it reverses the fluid valve 15 and so the direction of movement of the rotor and of the plate It. The extent to which the pawl arm 24 over-runs the pawl arm 25 when the latter is held up by the stop 33, is the measure of the extent to which the ratchet Wheel ii is moved on its clockwise movement more than on its anticlockwise movement. This amounts in effeet to a gradual movement of progression of the ratchet wheel 2| in a clockwise direction and therefore a similar movement of progression of the arms 25, 29 and 3% along the plate it, which has a fixed back and forth movement.

It follows therefore that the point at which an arm 28, 29 or 33 effects the reversal of the fluid valve 13 will vary at the end of each cycle of movements of the plate 15, dependin upon the extent of the progressive movements imparted to the ratchet wheel 25 during each cycle varying the position of the arm 28, 29 and 3t in the depressed part of the plate It. It will be noted that one end at of the depressed part 18 of the plate it has a gradual incline to the raised part ll of the plate, so that the roller on the arm 23, 29 or 33 can readily ride out of the depressed part, whilst another roller drops into the depressed part at its other end. The depressed part or part of reduced radius i8 ext-ends through an angular distance of approximately and the raised part through an angle of approximately 249. This is with an arrangement shown using three arms, 2s and Eli, but a different number of arms could be chosen which would give a different length of taper portion relative to the cylindircal portion of the bobbin being wound with a corresponding difference in the angles mentioned.

By adjusting the stop the extent of prcgression of the ratchet wheel 2! at each cycle of operations can be varied.

With the mechanism illustrated in Figures 1-3, the ring rail a, Figure 1, always commences its upward traverse or movement from a fixed point which is the bottom of the bobbin being wound.

The length of the traverse gradually decreases so as to build a bobbin with a tapered upper end and a cylindrical body.

It will be appreciated from a consideration of Figures 3 and 7, that the length of the traverse of the ring rail depends upon the position of the arm 28, 255 or (it (with its abutment piece 32) in the depressed part of the plate 56, when the said plate and the ratchet wheel 2i move together in clockwise direction in Figure 3 and an anticlockwise direction in Figure 7. As an arm with its abutment piece 32 approaches the end 5 3 of the depressed part, the length of traverse shortens. Finally one arm rides up the incline 35 out of the depressed part of the plate and ceases to operate the reversing valve. The next traverse is therefore a long one caused by the following arm with its abutm nt 32 dropping on to the other end of the depressed part of the plate it. In other words, the traverses of the ring rail gradually decrease in length from a maximum and then they increase to approximately the maximum in prevent unravelling ,of the yarn.

one cycle, which results in the laying upon the tapered end of the bobbin of'an open coil winding which acts to bind the previous windings and By a suitable choice of the pitch of the ratchet wheel teeth, in relation to the contour of the plate 15, it is possible to make the maximum traverse or stroke of the ring rail vary by a small amount, which is advantageous in preventing pattern winding at the end of the bobbin with consequent liability to unravelling during unwinding. 4

In the modification shown in Figures and 11, we provide for a progressive lengthening followed by a progressive shortening of the stroke of the vane or rotor of the hydraulic motor, so

that the traverses of the ring rail gradually increase in length to a maximum and then gradually shortens to a minimum. This produces a bobbin with a cylindrical body and a tapered end.

The lug or pin on the part acts in the same manner as the lug or pin 20 on the part it in the previous figures, to reverse the fluid control valve t at a definite point in the stroke of the vane of the motor. The part 40 is secured upon the motor shaft e as was the part l6 of the previously described construction. In this modification the ratchet wheel 4| has teeth of involute form and is engaged by two pawls 42, and 43 on arms44 and coupled by a spring 45. The arm 44 is secured upon the motor shaft as in the previous construction. When the arms and 45 are moving in an anticlockwise direction, the arm 45 engages the stop 4'! but the arm 44 goes back for its full traverse and carries with it by friction the ratchet wheel 4!, the double pawl 43 on the arm 45 rocking about its pivot to allow of such further movement of the ratchet wheel. The pawl 42 on the arm is withdrawn from the ratchet wheel 41 by the roller 49 on the arm 50, which terminates in the pawl 42, engaging the inclined track 48 before the arm 45 engages the stop 41. Upon reversal of move ment of the arm 44, whilst the pawl 42 is held out of engagement with the ratchet wheel, the spring 46 moves the arm 45 back into contact with the arm 44. It follows therefore that the ratchet wheel is moved by pawl 43 relative to the arm 44 at eachcycle, the amount of this movement depending on the distance which the arms 44 and 45 separate after the arm 45 has engaged the stop 47.

The pin or lug 53 on the ratchet wheel 4| engages the stop B on the rocking arm I to operate the reversing valve 12 at one end of the traverses or oscillating movements of the ratchet wheel.

Secured to the ratchet wheel 4| are adjustable stops or abutments 54 and 55 which are adapted to cause the double pawl 43 to turn about its pivot by engaging a projection 55 thereon to bring the other end of the pawl from that which was in service into engagement with the teeth of the ratchet wheel 4|. The spring 51 ensures that the pawl 43 moves from one position to another with a snap action.

If for example in Figures 10 and 11 the other end of the pawl 43 from that shown in service were engaging the ratchet wheel, then when the arm 45 engages the stop 41, the pawl 43 will prevent the ratchet wheel travelling forward with the arm 44. The result will be that the angular traverse of the ratchet wheel will be diminished at each'cycle until the pawl 43 is again turned about its pivot by the stop when such traverse will be increased, the one stop 54 acting to turn the pawl in one direction and the other stop 55 turning it in the other direction. By suitably adjusting the stops 54 and 55 around the ratchet wheel, the number of cycles of increasing and of diminishing traverses can be varied.

Our improved mechanism can be used for producing bobbins of varying shapes. The arrangement now to be described with reference to Figures 12-16 can produce bobbins which are tapered at both ends, such as are shown in full and dotted lines in Figure 15.

In Figures 12-14, the'ratchet wheel 2|, the pawl carrying arms 44 and 45 with their pawls 42 and 43 resemble the like parts shown in Figures 10 and 11 but in this case the reversing valve is operated by two stops 65 and 6| adjustably hired to the ratchet wheel 2|. It follows therefore that though the length of traverse or oscillation of the vane of the motor can be adjusted, it is, once the stops 55 and El have been clamped to the ratchet wheel, fixed. The double pawl 43 is reversed in position by the adjustable stops 54 and 55 on the ratchet wheel 2!, as with the previous construction, but the separation oi the pawl arms 44 and 45 which causes the ratchet wheel to move progressively in one direction and then progressively in the opposite direction is effected in a different manner, now to be described. When the hydraulic motor is turning the pawl arm 44 past the centre part of its oscillatory traverse, the roller 49 on the lever 5Q having the pawl 42 thereon engages the double inclined track 62 which removes the pawl 42 from the ratchet wheel. The latter is now carried'round by friction (as in Figures 10 and 11). A roller 63 on a bell crank lever 54 turning about the same axis as the pawl 42 and carried by the ratchet wheel 2| then engages the roller 6% which is in a fixed but adjustable position, which causes the roller 63 on said lever 54 to press the pawl arm 45 away from the pawl arm 44. This results in the ratchet wheel 2! bein advanced progressively in one or other direction (according to which end of the pawl 43 is engaging the ratchet wheel) until one or other or the stops 54 and 55 engages thepart 55 of the double pawl 43 and reverses it, as in the previously described arrangement.

It follows that this building motion gives a traverse of the ring rail which is of constant length but which is moved axially up and down the bobbin to give the desired tapered ends. This displacement of the constant length traverses is represented diagrammatically in Figure 16.

By varying the position of the roller 66 relatively to the roller on the bell crank lever 54, the extent of se'aration of the two pawl arms 44, 45 at each cycle of operations can be varied. The length of the tapered ends of the bobbin, as shown in Figure 15, can be varied by individually adjusting the stop 54, 55 in relation to the ratchet wheel 2!.

In Figure 17, the ring or spindle rails 15 are carried at the ends of cross beams?! connected to endless chains '52 and is which pass round upper chain wheels 74 and 15 on'intergeared shafts i5 and ii. The shaft 71 extends to the end of the machine and has the rotor of a vane type reversible motor thereon exactly as in the Figure 1 arrangement.

It will be appreciated that the shaft operated by the rotor of the vane type motor may operate spindle rails, ring rails, yarn traversing rods, traversing funnels or other devices used in textile machinery for giving the movements necessary to build a yarn package of any desired shape.

What We claim is:

l. A building motion for the building of yarn packages in textile machines comprising a reversing vane type hydraulic motor, a motor shaft therefor, a vane rigidly carried by the shaft and movable back and forth in the space between the shaft and the motor casing, a fixed abutment in the space between the shaft and motor casing and in the path of movement of the vane, fluid inlet and fluid outlet ports in opposite faces of said abutment, a pinion on said shaft, means for traversing the yarn along the yarn packages which are being wound, a drive connection between the said pinion and said means to reciprocate said traversing means, a reversing valve controlling the fluid flow to and from the ports in the abutment mounted directly on the motor casing for reversing the direction of oscillation of the said vane, spring actuated means operatively coupled to the said reversing valve to move such valve from one extreme position to the other extreme position with a snap action, whereby the openin and closing of the ports is substantially instantaneous, means actuated by the motor shaft for operating said valve and means for varying the relative positions of reversal of the vane in order to vary the length of traverses of the yarn on the yarn packages.

2. A building motion as claimed in claim 1 in which the means actuated by the motor shaft for operatin the valve vary the relative pos1- tions of successive traverses of the yarn on the yarn packages.

3. A building motion as claimed in claim 1 having a spindle for said reversing valve, a crank 1 arm on the reversing valve spindle, a disc driven by the motor shaft, an abutment upon said disc engaging said crank arm and reversing the valve at the end of one direction of movement of the vane, a ratchet wheel having peripheral teeth frictionally driven by the motor shaft, a pawl carrying arm turning with the motor shaft, a pawl on said arm engagin the peripheral teeth of the ratchet wheel, a second pawl carrying arm connected to the aforesaid pawl carrying arm by a spring and movable therewith about the axis of the motor shaft, a pawl on the second pawl carrying arm also engaging the peripheral teeth of the ratchet wheel, adjustable means limiting the movement of the second pawl carrying arm in the direction in which the motor shaft moves to cause the abutment on the aforesaid disc to reverse the valve, the stopping of the said second pawl carrying arm causing the stoppage of the ratchet wheel also, the first pawl carrying arm moving the ratchet wheel through out its return stroke with the motor shaft so that the ratchet wheel moves through a greater angular distance in on direction than the other and thus advances gradually in one direction and means connected with the ratchet wheel operating the reversing valve in the opposite direction to that in which it is moved by the aforesaid abutment.

i. A building motion as claimed in claim 3, in which the ratchet wheel has arms pivotally mounted thereon, a cam plate with raised and depressed peripheral parts turnable with the motor shaft, the said arms being equally spaced around and riding under sprin pressure on the periphery of the cam plates, the one of said arms'which is riding on the depressed part of the cam plate periphery operatin the valve to reverse the motor.

5. A building motion as claimed in claim 1 having a spindle for the reversing valve, a crank arm on the reversing valve spindle, a part driven by the motor shaft operating said crank arm to reverse the valve at the end of one direction of movement of the vane, a ratchet wheel having peripheral teeth frictionally driven by the motor shaft, a pawl carrying arm turning with the motor shaft, a pawl on said arm engagin the peripheral teeth of the ratchet wheel, the pawl having an extension beyond its pivot, a second pawl carrying arm connected to the aforesaid pawl carrying arm by a spring and movable therewith about the axis of the motor shaft, a pawl on said second pawl carrying arm, said second pawl being double ended with a sprin to hold one or other end in action with the pawl engagin the ratchet wheel, adjustable means on the said ratchet wheel reversing the said double ended pawl, adjustable means limiting the movement of the second pawl carrying arm in the direction in which the motor shaft moves to cause the said part driven by the motor shaft to reverse the valve, means placing the pawl on the first mentioned pawl carrying arm out of action after the motion of the second pawl carrying arm has been arrested with consequent arrest of the movement of the ratchet wheel so that the ratchet wheel travels a shorter distance in one direction than the other and means whereby the ratchet wheel operates the reversing valve in one direction, the reversals of the double ended pawl giving gradually increasin lengths of movement of the ratchet wheel followed by gradually reducing lengths thereof with corresponding variations in the lengths of rotor traverses.

6. A building motion as claimed in claim 5 in which the ratchet wheel has arm pivotally mounted thereon, a cam plate with raised and depressed peripheral parts turnable with the 1 motor shaft, the said arms bein equally spaced around and riding under spring pressure on the periphery of the cam plate, the one of said arms which is riding on the depressed part of the cam plate periphery operating the valve to reverse the motor.

7. A building motion as claimed in claim 1 having a spindle for the reversing valve, a crank arm on the reversing valve spindle, a ratchet wheel having peripheral teeth frictionally driven by the motor shaft, a pawl carrying arm turning with the motor shaft, a pawl on said arm engaging the peripheral teeth of the ratchet wheel, the pawl having an extension beyond its pivot, a second pawl carrying arm connected to the aforesaid pawl carrying arm by a sprin and movable therewith about the aXis of the motor shaft, a pawl on said second pawl carrying arm, said second pawl being double ended with a sprin to hold one or other end in action with the pawl engaging the ratchet wheel, adjustable means on the said ratchet wheel reversing the said double ended pawl, adjustabl means limiting the movement of the second pawl carrying arm, means upon said ratchet wheel actuat ing said crank arm at the ends of its back and forth movements, means placing the pawl on the first mentioned pawl carrying arm out of action after the motion of the second pawl carrying arm has been arrested with consequent arrest of the movement of the ratchet wheel so that the ratchet wheel travels a shorter distance in one direction than the other and then reverses the direction in which the shorter distances occur and thus the ratchet wheel advances progressively in one direction and then in the other direction and the consequent yarn traverses are kept of constant but adjustable length and moved axially up and down the package being wound.

References Cited in the file of this patent UNITED STATES PATENTS Number Number Name Date Barrett Mar. 17, 1942 Nickles Jan. 23, 1951 Smith Nov. 13, 1951 Killoran Nov. 20, 1951 FOREIGN PATENTS Country Date Great Britain May 26, 1883 Switzerland July 1, 1936 Great Britain July 11, 1949 

